lecture 5 internal forces in beams in plane bending
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LECTURE 5 Internal Forces in Beams in Plane Bending Deformation. Diagrams of Internal Forces
Introduction
A bar subjected to bending is called a beam.
Let us consider a model of bending when a plane of bending load coincides with
one of cross-sectional principal planes. This type of bending is sometimes called
simple bending. Actually, it is plane bending. The examples of plane bending
deformation are shown on Fig. 1.
Fig. 1
It is usual to distinguish pure bending (Fig. 2) and transverse bending (Fig. 3).
Pure bending is a type of loading producing the only bending moment ( yM or zM ) in
cross-section of a rod. In transverse bending, both shearing force ( zQ or yQ ) and
bending moment ( yM or zM ) occur in a rod section. The examples of pure plane
bending and transverse plane bending are shown on Figs. 2 and 3, respectively.
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Fig. 2
Fig. 3
1 Types of beam supports
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There are three main types of beam supports:
1. Movable hinged (pin) support;
2. Immobile hinged support;
3. Rigidly fixed (built-in) support.
The force factors that appear in supports are called support reactions.
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A. Illustration of movable hinged (pin) support
A movable hinged support (Fig. 4) permits free axial displacement of the beam
on rollers that’s why the only one support reaction appears into it. This reaction is
directed perpendicularly to support plane.
B. Illustration of immovable hinged (pin) support
At immobile hinged support, the reaction is directed to the horizontal axis at an
arbitrary angle ; this reaction can be resolved into two reaction components along the
horizontal and vertical axes (see Fig. 5).
Fig. 4
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The first two types of supports permit free rotation of the beam in support cross-
section, and therefore, no support moments appear in them (Figs. 4, 5). Only a rigidly
fixed (built-in) support, which does not permit the beam cross-section to rotate, can
create a reactive support moment (Fig. 6).
C. Illustration of rigidly fixed support
A rigidly fixed support gives three reactions: RM , vR , hR (see Fig. 6).
As a rule, the beam is in equilibrium, and therefore, three equilibrium equations are
used to describe this balance:
0 xF , 0 zF , 0M . (1)
Equations (1) are used to determine support reactions.
Fig. 5
Fig. 6
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2 The Sign Conventions in Internal Forces Calculation by Method of Sections
Fig. 7
If an external force applied to the left of the section m-m is directed upwards, the
shearing force at the section is considered to be positive 0mQ , otherwise negative
0mQ . It means, that the forces tend to produce clockwise rotation (Fig. 7) create
0mQ ; the forces tend to produce counter-clockwise rotation create 0mQ .
Fig. 8
The rule of signs for determining the bending moment can be formulated as follows: a
moment in cross-section n-n is considered to be positive if it affects the beam in the
way it becomes convex downwards, and vice versa (Fig. 5).
3 Shear Force and Bending Moment Diagrams for Cantilevers
Let us determine the internal force factors in an arbitrary section. To do this, the
beam is cut mentally through the section and the unknown internal force factors Qz and
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My are applied in the section to produce an equilibrium of any part of the beam under
consideration.
The equilibrium equations for the cut-off portion of the beam are as follows:
0 zF , 0 yM . (2)
In all cases, the shearing force for a prismatic rod is equal to the algebraical sum of all
external forces projections on the plane of section lying on one side of the section (left
or right). The bending moment at a section may be regarded as the sum of moments, in
relevance to the transverse axis in the section, of all forces applied to one side of this
section (left or right). In designing of bending moment and shearing force diagrams
with one tip fixed it is possible not to find the reactions in rigidly fixed support. Beams
of this kind are commonly called cantilevers.
Rule We will lay off the values of the bending moments from tensioned fibers of a
bent beam.
Fig. 9
Example 1 Internal forces
induced by concentrated external
moment
Given: M, l.
R.D.: zQ x , yM x .
Equations of internal force factors
are: I-I: 0 x l
0IzQ x ,
IyM x M .
The diagrams are design on Fig. 9.
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Fig. 10
Example 2 Internal forces
induced by concentrated external
force
Given: F, l.
R.D: zQ x , yM x .
Equations of internal force factors
are: I-I: 0 x l
IzQ x F ,
0
0Iy x x l
M x Fx Fl
.
The diagrams are design on Fig. 10.
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Example 3 Internal forces induced by uniformly distributed external load
Given: q, l, where q is the intensity
of uniformly distributed loading.
R.D.: zQ x , yM x .
The resultant ( qR ) of the uniformly
distributed load q is equal to the area of
the diagram q(x) and this resultant
passes through the “center of gravity” of
this diagram.
The shearing force diagram is
represented by a straight line. As may
be seen from expression (3) the shearing
force Qz in portion I-I increases from 0
to ql (0 x l ):
00 .
Iz q
x x l
Q x R
qx ql (3)
The maximum value of the shearing
force occurs at the built-in support.
The sum of the moments of external
forces lying on one (right) side of the
section is
2 2
0
02 2 2
Iy q x l
x
x qx qlM x R
, (4)
where qx is the resultant of uniformly distributed load q of x length. This resultant
passes through the midpoint of the segment x. Consequently, the arm of the force is
x/2, and the moment of this force is equal to 2
2 2 q
x xR q .
The bending moment diagram is represented by parabola. The maximum value of the
bending moment occurs at the built-in support. The graphs zQ x and yM x are
design on Fig. 11.
Fig. 11
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Example 4 Internal forces induced by linearly distributed external load
with increased intensity
Given: qm, l (qm is maximum intensity
of distributed load).
R.D.: zQ x , yM x .
Let’s consider the part of distributed
load with the maximum magnitude q(x)
applied to the right part of the beam:
Using similarity of the triangles:
m
m
q x q xxq x
q l l,
I-I: 0 x l
2
0
02 2
Iy q x l
x
qx qlQ x R
l
3
0
10
3 6
Iy q x l
x
qxM x R x
l
2
6
ql.
The graphs zQ x and yM x are
design on Fig. 12.
Fig. 12
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Example 5 Internal forces created
by linearly distributed external load with
decreased intensity
Given: qm, l.
R.D: zQ x , yM x – ?
To simplify the solution of this problem let
us apply two equal in magnitude but
oppositely directed linearly distributed
loads of the same intensity. One load is
directed downwards and the other is
directed upward. Thus, we have static zero
in any cross-section. This method alloys to
use two previous examples to solve the
problem:
I-I: 0 x l
2
0
0 ,2 2 2
Iy x l
x
qx ql qlQ x qx ql
l
2 3 2
0
02 6 3
Iy x l
x
qx qx qlM x
l.
The graphs zQ x and yM x are design
on Fig. 13.
Fig. 13
MINISTRY OF EDUCATION AND SCIENCE OF UKRAINE
National aerospace university “Kharkiv Aviation Institute”
Department of aircraft strength
Course Mechanics of materials and structures
HOME PROBLEM 4
Graphs of Shear Force and Bending Moment Distribution in Plane Bending (Cantilevers)
Name of student:
Group:
Advisor:
Data of submission:
Mark:
13
Shear force in a prismatic rod is
equal to the algebraic sum of all
external forces projections on the
cross-section lying on one side of the
section (left or right).
The bending moment at a section
is equal to the sum of moments, in
relevance to the transverse axis in the
section, of all external forces applied
to one side of the section (left or
right).
Solution
1. Accepting the sign conventions in internal forces calculating.
(a) for shear force (b) for bending moment
Fig. 1
2. Writing the equations of shear force and bending moment functions in an arbitrary
sections of each potion (see Fig. 2).
Note. Method of sections will be applied from the right free tip of the cantilever and the
cross-sections will be established at x-distance relative to origin of each potion.
0m mzQ 0m m
zQ 0m myM 0m m
yM
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I – I (0 ) :x a
0 2
( ) 0 20Iz
x xQ x qx
kN,
0 2
( ) 20 02
Iy
x x
xM x M qx
kNm.
II – II (0 ) :x b
0 2
( ) 20 20IIz
x xQ x qa
kN,
0 2
( ) 0 402
IIy
x x
aM x M qa x
kNm.
III – III (0 ) :x c
0 2
( ) 10 10IIIz
x xQ x qa P qx
kN,
Note, that the change of shear force sign within the boundaries of this section predicts the
bending moment extreme value, since the derivative of bending moment is equal to shear
force:
( ( ))( ) .
IIIy III
z
d M xqa P qx Q x
dx
Therefore, zero shear force and also zero bending moment derivative represent the point of
bending moment extreme value.
To find it, let us determine the coordinate of zero shear force ex and substitute it into
bending moment equation.
1 30 10 2( ) 0 ( ) 1m
10
IIIz e e eQ x qa P qx x P qa
q
.
0 2
( ) 40 402 2
IIIy
x x
q xM x M qa a x Px qx
kNm.
max
2
( ) 352 2
III III ey e e ey
qxqM x M M qa a x Px
kNm.
3. Designing the graphs of shear forces and bending moments. Positive shear forces will
be drawn upwards and vice versa. Bending moment graph will be drawn on tensile fibers
according to the sign convention mentioned above (see Fig. 1 right). The graphs are shown
on Fig. 2.
4. Applying the shear force and bending moment values in the rigid support as
corresponding reactions according to accepted sign conventions (see Fig. 2).